US20190301777A1 - Heat source system, control device, control method, and program - Google Patents

Heat source system, control device, control method, and program Download PDF

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Publication number
US20190301777A1
US20190301777A1 US16/467,011 US201716467011A US2019301777A1 US 20190301777 A1 US20190301777 A1 US 20190301777A1 US 201716467011 A US201716467011 A US 201716467011A US 2019301777 A1 US2019301777 A1 US 2019301777A1
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Prior art keywords
path
load
cooling tower
heat
heat exchange
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US16/467,011
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English (en)
Inventor
Masanobu Sakai
Satoru Tani
Kiyokazu TSUJI
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Assigned to MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SAKAI, MASANOBU, TANI, SATORU, TSUJI, KIYOKAZU
Publication of US20190301777A1 publication Critical patent/US20190301777A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D13/00—Stationary devices, e.g. cold-rooms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/29—High ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • the present invention relates to a heat source system, a control device, a control method, and a program.
  • Patent Literature 1 describes a heat source machine system that aims to drive the heat source machine always in a rated driving range and stabilize a driving state regardless of a heat demand on a heat load side.
  • a cooling tower or heating tower is connected to the heat source machine through an outward path and a return path.
  • a heat load is connected to the heat source machine through the outward path and the return path.
  • the return path from the cooling tower or the heating tower and the return path from the heat load are connected to a heat exchanger.
  • the heat exchanger performs heat exchange between the return path from the cooling tower or the heating tower and the return path from the heat load.
  • temperature control of the cooling water supplied to the heat source machine is complicated in that the temperature of the cooling water from the cooling tower or the heating tower changes due to the heat exchange.
  • accuracy of the temperature control of the cooling water is reduced, accuracy of temperature control of cold water supplied by the heat source machine system may be reduced.
  • the temperature of the cooling water may fall below the lower limit value, and the heat source machine may stop.
  • the present invention provides a heat source system, a control device, a control method, and a program capable of continuing driving of a heat source machine even in a case in which a cold heat amount required by a heat load is small, and relatively simply performing temperature control of cooling water.
  • a heat source system includes a heat source machine, a cooling tower side outward path and a cooling tower side return path that are connected to the heat source machine, a load side outward path and a load side return path that are connected to the heat source machine, a heat exchange path provided in one of the load side return path and the cooling tower side outward path, a heat exchanger that performs heat exchange between the heat exchange path and the other one of the load side return path and the cooling tower side outward path, and a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path.
  • the heat source system may include a cooling tower bypass path connecting the cooling tower side outward path and the cooling tower side return path with each other, and a cooling tower bypass valve capable of adjusting a flow rate of the cooling tower bypass path.
  • the heat exchange path may be provided on the load side return path, and the heat exchanger may be disposed in the cooling tower side outward path at a position closer to the heat source machine than the cooling tower bypass path.
  • the heat source system may include a cooling tower bypass path connecting the cooling tower side outward path and the cooling tower side return path with each other, and a cooling tower bypass valve capable of adjusting a flow rate of the cooling tower bypass path.
  • the heat exchange path may be provided in the cooling tower side outward path at a position closer to the heat source machine than the cooling tower bypass path.
  • the heat source system may include a load determination unit that determines whether or not a load of cold heat supply from the heat source machine is less than a load lower limit value, and a driving control unit that causes the heat exchanger to perform the heat exchange by controlling the heat exchange adjustment valve in a case in which the load determination unit determines that the load of the cold heat supply from the heat source machine is less than the load lower limit value.
  • a control device is a control device that controls a heat source system including a heat source machine, a cooling tower side outward path and a cooling tower side return path that are connected to the heat source machine, a load side outward path and a load side return path that are connected to the heat source machine, a heat exchange path provided in one of the load side return path and the cooling tower side outward path, a heat exchanger that performs heat exchange between the heat exchange path and the other one of the load side return path and the cooling tower side outward path, and a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path.
  • the control device includes a load determination unit that determines whether or not a load of the heat source machine is less than a load lower limit value, and a driving control unit that causes the heat exchanger to perform the heat exchange by controlling the heat exchange adjustment valve in a case in which the load determination unit determines that the load of the heat source machine is less than the load lower limit value.
  • a control method includes determining whether or not a load of a heat source machine of a heat source system is less than a load lower limit value, the heat source system comprising the heat source machine, a cooling tower side outward path and a cooling tower side return path that are connected to the heat source machine, a load side outward path and a load side return path that are connected to the heat source machine, a heat exchange path provided in one of the load side return path and the cooling tower side outward path, a heat exchanger that performs heat exchange between the heat exchange path and the other one of the load side return path and the cooling tower side outward path, and a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path, and causing the heat exchanger to perform the heat exchange by controlling the heat exchange adjustment valve in a case in which it is determined that the load of the heat source machine is less than the load lower limit value.
  • a program is for a computer that controls a load of a heat source machine of a heat source system comprising the heat source machine, a cooling tower side outward path and a cooling tower side return path that are connected to the heat source machine, a load side outward path and a load side return path that are connected to the heat source machine, a heat exchange path provided in one of the load side return path and the cooling tower side outward path, a heat exchanger that performs heat exchange between the heat exchange path and the other one of the load side return path and the cooling tower side outward path, and a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path, the program causes the computer to execute determining whether or not the load of the heat source machine is less than a load lower limit value, and causing the heat exchanger to perform the heat exchange by controlling the heat exchange adjustment valve in a case in which it is determined that the load of the heat source machine is less than the load lower limit value.
  • the control device According to the heat source system, the control device, the control method, and the program described above, it is possible to continue driving of the heat source machine even in a case in which a cold heat amount required by a heat load is small, and it is possible to relatively simply perform temperature control of cooling water.
  • FIG. 1 is a schematic block diagram showing a functional constitution of a heat source system according to an embodiment.
  • FIG. 2 is a schematic constitution diagram showing an example of a device constitution of a freezer plant main body 200 according to the embodiment.
  • FIG. 3 is a graph showing a driving range of a turbo freezer 300 according to the embodiment.
  • FIG. 4 is a flowchart showing an example of a process procedure in which a control device 100 controls the freezer plant main body 200 according to the embodiment.
  • FIG. 5 is a schematic constitution diagram showing another example of the device constitution of the freezer plant main body 200 according to the embodiment.
  • FIG. 1 is a schematic block diagram showing a functional constitution of a heat source system according to the embodiment.
  • the heat source system 1 includes a control device 100 and a freezer plant main body 200 .
  • the control device 100 includes a communication unit 110 , a storage unit 180 , and a control unit 190 .
  • the control unit 190 includes a load determination unit 191 and a driving control unit 192 .
  • the heat source system 1 supplies cold heat to a heat load. Specifically, the heat source system supplies cold water to the heat load. That is, the heat source system 1 supplies the cold heat to the heat load using water as a medium.
  • the cold water supplied to the heat load by the heat source system 1 corresponds to an example of the cold heat.
  • the heat source system 1 While a freezer included in the freezer plant main body 200 stops at a light load, the heat source system 1 stably supplies the cold water even in a case in which a cold water amount required by the heat load rapidly increases from a small cold water amount. In a case in which the freezer stops at the light load, it takes time to activate the freezer again, and in a case in which the cold water amount required by the heat load rapidly increases, there is a possibility that the cold heat amount that is able to be supplied may be insufficient, or a possibility that cold water at a temperature required by the heat load may not be able to be supplied. Therefore, the heat source system 1 has a mechanism and a mode in which the freezer is not stopped even at the light load.
  • the control device 100 controls the freezer plant main body 200 .
  • a driving mode in which the control device 100 controls the freezer plant main body 200 includes a normal mode and a simulation load mode.
  • the driving mode in which the control device 100 controls the freezer plant main body 200 is also referred to as a driving mode of the freezer plant main body 200 .
  • the control device 100 is constituted using, for example, a computer such as a programmable logic controller (PLC) or a general work station.
  • PLC programmable logic controller
  • the communication unit 110 communicates with the freezer plant main body 200 .
  • the communication unit 110 transmits a control signal to the freezer plant main body 200 , and receives measured values by various sensors of the freezer plant main body 200 .
  • the storage unit 180 stores various pieces of data.
  • the storage unit 180 is constituted using a storage device included in the control device 100 .
  • the control unit 190 controls each unit of the control device 100 to execute various processes.
  • the control unit 190 is constituted, for example, by a central processing unit (CPU) included in the control device 100 , which reads a program from the storage unit 180 and executes the program.
  • CPU central processing unit
  • the load determination unit 191 determines whether or not the load of the heat source machine of the freezer plant main body 200 is less than a load lower limit value.
  • the load lower limit value described here is a threshold value that is a determination reference of whether or not to stop the driving of the freezer at the light load in the normal mode.
  • the driving control unit 192 performs various arithmetic operations for controlling the freezer plant main body 200 .
  • the driving mode of the freezer plant main body 200 is the simulation load mode and the load determination unit 191 determines that the load of the heat source machine of the freezer plant main body 200 is less than the load lower limit value
  • the driving control unit 192 controls the freezer plant main body 200 so as not to stop the freezer of the freezer plant main body 200 .
  • the freezer plant main body 200 includes a heat exchanger that receives heat from the freezer as a simulated heat load, and the driving control unit 192 controls a heat exchange adjustment valve connected to the heat exchanger to cause the heat exchanger to perform the heat exchange. A load at which the freezer supplies the cold water is increased due to this heat exchange, and the freezer continues the driving without the light load stop.
  • FIG. 2 is a schematic constitution diagram showing an example of a device constitution of the freezer plant main body 200 .
  • the freezer plant main body 200 includes a turbo freezer 300 , a cooling tower 410 , a cooling water pump 420 , a cooling tower side three-way valve 430 , a heat exchanger 500 , a cold water pump 620 , a heat load side three-way valve 630 , an outward path side temperature sensor 711 , a return path side temperature sensor 712 , and a flow rate sensor 721 .
  • the turbo freezer 300 includes an evaporator 310 , an evaporator pump 320 , a turbo compressor 330 , a condenser 340 , a refrigerant pump 350 , and an expansion valve 360 .
  • the freezer plant main body 200 is connected to a heat load 610 .
  • the freezer plant main body 200 operates in accordance with control of the control unit 190 , and supplies the cold water to the heat load 610 .
  • the turbo freezer 300 corresponds to an example of the heat source machine, and supplies the cold water to the heat load 610 in response to a request from the heat load 610 .
  • the turbo freezer 300 is designed to stop at the time of the light load. In a case in which the load of the turbo freezer 300 is the load lower limit value, the turbo freezer 300 is stopped in accordance with the control of the control device 100 .
  • the heat source machine included in the freezer plant main body 200 is not limited to the turbo freezer, and may be any heat source machine that stops at the time of the light load.
  • the freezer plant main body 200 may include a heat source machine capable of supplying both of hot water and cold water to the heat load 610 .
  • the evaporator 310 performs heat exchange between the refrigerant of the turbo freezer 300 and the cold water supplied to the heat load 610 .
  • the evaporator 310 evaporates the refrigerant and reduces the temperature of the cold water by evaporation heat.
  • the evaporator 310 sprays the refrigerant toward a pipe from a spray port provided above the pipe through which the cold water flows.
  • a refrigerant first path W 31 is a path connecting a lower portion of the evaporator 310 and the spray port with each other.
  • An evaporator pump 320 is provided in the refrigerant first path W 31 , and the evaporator pump 320 causes liquid refrigerant accumulated in the evaporator 310 to flow to the spray port.
  • the refrigerant gasified by the evaporator 310 flows to the turbo compressor 330 through a refrigerant second path W 32 and is compressed.
  • the gaseous refrigerant of which pressure and a temperature are increased by the compression flows to the condenser 340 through a refrigerant third path W 33 .
  • the condenser 340 cools and liquefies the refrigerant by performing the heat exchange between the gaseous refrigerant compressed by the turbo compressor 330 and the cooling water.
  • the refrigerant that has become liquid returns to the evaporator 310 through a refrigerant fourth path W 34 .
  • a refrigerant pump 350 and an expansion valve 360 are provided in the fourth refrigerant path W 34 , and the refrigerant pump 350 transfers the liquid refrigerant from the condenser 340 to the evaporator 310 .
  • the refrigerant is easily evaporated by being decompressed by the expansion valve 360 .
  • the turbo freezer 300 is stopped at the light load in accordance with the specification of the turbo compressor 330 .
  • FIG. 3 is a graph showing a driving range of the turbo freezer 300 .
  • a horizontal axis of the graph of FIG. 3 indicates a load factor of the turbo freezer 300 .
  • a vertical axis indicates driving possibility or impossibility of the turbo freezer 300 .
  • the turbo freezer 300 is able to be driven at a load factor of 30% or more. That is, the driving range of the turbo freezer 300 is a load factor of 30% or more.
  • the turbo freezer 300 is stopped.
  • the heat exchanger 500 receives the cold water supplied to the turbo freezer 300 at the time of the light load of the turbo freezer 300 , and thus the load of the turbo freezer 300 is increased. Therefore, the turbo freezer 300 is able to continue the driving even at the light load, and is able to supply the required amount of cold water to the heat load.
  • the turbo freezer 300 is connected to the cooling tower 410 through a cooling tower side outward path W 11 and a cooling tower side return path W 12 .
  • the cooling tower 410 exchanges heat with the refrigerant in the condenser 340 of the turbo freezer 300 to cool the heated cooling water.
  • the cooling tower side outward path W 11 is a path through which the cooling water heated by the condenser 340 flows to the cooling tower 410 .
  • the cooling tower side return path W 12 is a path through which the cooling water cooled by the cooling tower 410 flows to the condenser 340 .
  • the cooling water pump 420 circulates the cooling water between the turbo freezer 300 and the cooling tower 410 .
  • the cooling water pump 420 is provided in the cooling tower side return path W 12 , and the cooling water flows from the cooling tower 410 to the turbo freezer 300 .
  • the turbo freezer 300 is connected to the heat load 610 through a load side outward path W 21 and a load side return path W 22 .
  • the load side outward path W 21 is a path through which the cold water cooled by the evaporator 310 of the turbo freezer 300 flows to the heat load 610 .
  • the load side return path W 22 is a path through which the cold water used at the heat load 610 and of which temperature has increased flows to the evaporator 310 .
  • the cold water pump 620 circulates the cold water between the turbo freezer 300 and the heat load 610 .
  • the cold water pump 620 is provided in the load side return path W 22 and causes the cold water to flow from the heat load 610 to the turbo freezer 300 .
  • the heat load 610 may return all the cold water supplied from the evaporator 310 to the evaporator 310 .
  • the heat load 610 may take some or all of the cold water and not return the cold water to the evaporator 310 .
  • water may be supplied to the evaporator 310 from a water supply source, such as a water supply, instead of the cold water taken by the heat load 610 .
  • the supplied water may be normal temperature water.
  • the heat exchanger 500 is provided in the cooling tower side outward path W 11 .
  • the heat exchanger 500 is connected to the load side return path W 22 through a heat exchange path W 23 .
  • the heat exchanger 500 performs heat exchange between the cooling tower side outward path W 11 and the load side return path W 22 by performing heat exchange between the cooling tower side outward path W 11 and the heat exchange path W 23 .
  • the cold water branched from the load side return path W 22 to the heat exchange path W 23 absorbs heat from the cooling water flowing through the cooling tower side outward path W 11 . Due to this heat absorption, the temperature of the cold water returning to the turbo freezer 300 is increased, and the load by which the turbo freezer 300 supplies the cold water to the heat load 610 is increased. Therefore, even in a case in which the cold water amount required by the heat load 610 is small, the load of the turbo freezer 300 becomes equal to or greater than the load lower limit value, and the turbo freezer 300 continues the driving.
  • the load side return path W 22 and the heat exchange path W 23 are connected through a heat load side three-way valve 630 .
  • the heat load side three-way valve 630 is a flow rate adjustment valve corresponding to an example of the heat exchange adjustment valve, and adjusts the amount of the cold water branched from the load side return path W 22 to the heat exchange path W 23 .
  • the heat load side three-way valve 630 is also able to set the flow rate from the load side return path W 22 to the heat exchange path W 23 to zero. Therefore, the branch of the cold water from the load side return path W 22 to the heat exchange path W 23 is blocked.
  • two two-way valves may be used to perform control similar to that of the three-way valve. The same applies to the other three-way valves.
  • a cooling tower bypass path W 13 is provided between the cooling tower side outward path W 11 and the cooling tower side return path W 12 .
  • the temperature of the cooling water flowing to the condenser 340 is able to be adjusted by bypassing some of the cooling water flowing through the cooling tower side outward path W 11 to the cooling tower side return path W 12 by the cooling tower bypass path W 13 .
  • the cooling tower side outward path W 11 and the cooling tower bypass path W 13 are connected with each other through a cooling tower side three-way valve 430 .
  • the cooling tower side three-way valve 430 is a flow rate adjustment valve corresponding to an example of a cooling tower bypass valve, and adjusts the amount of the cooling water bypassed from the cooling tower side outward path W 11 to the cooling tower side return path W 12 .
  • the cooling tower side three-way valve 430 is also able to set the flow rate of the cooling water from the cooling tower side outward path W 11 to the cooling tower bypass path W 13 to zero. Therefore, the bypass of the cooling water from the cooling tower side outward path W 11 to the cooling tower side return path W 12 is blocked.
  • the cooling tower side three-way valve 430 is provided on a downstream side of the heat exchanger 500 in the cooling tower side outward path W 11 .
  • the downstream side of the heat exchanger 500 in the cooling tower side outward path W 11 is a side closer to the cooling tower 410 as viewed from the condenser 340 .
  • the cooling water flows through the cooling tower side three-way valve 430 after the heat exchange in the heat exchanger 500 .
  • the temperature of the cooling water passing through the cooling tower side three-way valve 430 does not change through the heat exchanger 500 before reaching the condenser 340 .
  • the control unit 190 calculates a bypass amount of the cooling water on the basis of the temperature of the cooling water in the cooling tower side three-way valve 430 , it is not necessary to consider the temperature change of the cooling water due to the heat exchanger 500 . At this point, it is possible to avoid an increase of a load for which the control unit 190 calculates the bypass amount of the cooling water.
  • the outward path side temperature sensor 711 is provided in the load side outward path W 21 , and measures the temperature of the cold water flowing through the load side outward path W 21 .
  • the return path side temperature sensor 712 is provided in the load side return path W 22 , and measures the temperature of the cold water flowing through the load side return path W 22 .
  • the flow rate sensor 721 is provided in the load side outward path W 21 , and measures the flow rate of the cold water flowing through the load side outward path W 21 .
  • a value obtained by multiplying a temperature difference obtained by subtracting the temperature measured by the outward path side temperature sensor 711 from the temperature measured by the return path side temperature sensor 712 by the flow rate measured by the flow rate sensor 721 indicates a cold water heat amount consumed by the heat load 610 . That is, the cold water heat amount QI_CH consumed by the heat load 610 is expressed by Formula (1).
  • TI_CHo indicates a cold water outlet temperature.
  • TI_CHi indicates a cold water inlet temperature.
  • FI_CH indicates a cold water flow rate.
  • the cold water flow rate it is possible to use the flow rate of the cold water in the load side outward path W 21 measured by the flow rate sensor 721 .
  • FIG. 4 is a flowchart showing an example of a process procedure in which the control device 100 controls the freezer plant main body 200 .
  • the control device 100 performs the process of FIG. 4 in a case in which a driving start operation that is a user operation instructing to start the driving of the heat source system 1 is performed.
  • the driving control unit 192 of the control device 100 activates the turbo freezer 300 (step S 101 ).
  • the driving control unit 192 waits for a lapse of a t 2 time from the start of the activation of the turbo freezer 300 (step S 102 ), and further waits for a lapse of a t 1 time (step S 103 ).
  • the t 1 time is a control determination period in the control device 100 .
  • the control determination period referred to here is a period in which the driving control unit 192 repeats the process of determining the driving mode of the freezer plant main body 200 and controlling the freezer plant main body 200 .
  • the t 2 time is an activation time of the turbo freezer 300 . Specifically, the t 2 time is an effect waiting time from the start of the activation of the turbo freezer 300 to appearance of the effect of cooling.
  • step S 103 is not essential. Therefore, after waiting for the t 2 time in step S 102 , the driving control unit 192 may shift to step S 104 without waiting for the time in step S 103 .
  • the driving control unit 192 determines the driving mode of the freezer plant main body 200 (step S 104 ). For example, the driving control unit 192 calculates the cold water heat amount QI_CH consumed by the heat load 610 on the basis of Formula (1) described above. In addition, the driving control unit 192 determines the driving mode by comparing the calculated cold water heat amount QI_CH with a heat amount lower limit value Qmin. In a case in which Formula (2) is established, the driving control unit 192 determines that the driving mode of the freezer plant main body 200 is the normal mode.
  • h 1 indicates a coefficient for hunting prevention.
  • the driving control unit 192 determines that the driving mode of the freezer plant main body 200 is the simulation load mode.
  • h 2 indicates a coefficient for hunting prevention.
  • the heat amount lower limit value Qmin may be determined in advance as a constant value.
  • the control device 100 may communicate with the turbo freezer 300 to receive the heat amount lower limit value Qmin.
  • the driving control unit 192 may determine the driving mode on the basis of the cold water inlet temperature Ti_CHi and the temperature lower limit Tmin, instead of the cold water heat amount QI_CH and the heat amount lower limit value Qmin. For example, in a case in which Formula (4) is established, the driving control unit 192 determines that the driving mode of the freezer plant main body 200 is the normal mode.
  • h 3 indicates a coefficient for hunting prevention.
  • the driving control unit 192 determines that the driving mode of the freezer plant main body 200 is the simulation load mode.
  • h 4 indicates a coefficient for hunting prevention.
  • step S 104 the driving control unit 192 performs simulation load driving control (step S 111 ).
  • the driving control unit 192 adjusts the flow rate of the cold water flowing through the heat exchanger 500 by controlling the heat load side three-way valve 630 so that the cold water heat amount QI_CH obtained by Formula (1) becomes equal to or greater than the heat amount lower limit value Qmin.
  • the driving control unit 192 waits for the lapse of the t 2 time (step S 112 ). In addition, the driving control unit 192 determines whether or not a driving end operation has been performed (step S 131 ).
  • the driving end operation referred to here is a user operation instructing an end of the driving of the heat source system 1 .
  • step S 131 NO
  • the process returns to step S 104 .
  • step S 131 the driving control unit 192 stops the turbo freezer 300 (step S 141 ).
  • the driving control unit 192 ends the control of the freezer plant main body 200 (step S 142 ).
  • step S 142 the process of FIG. 4 is ended.
  • step S 104 in a case in which it is determined that the driving mode is the normal mode (step S 104 : normal mode), the driving control unit 192 performs normal driving control (step S 121 ).
  • the driving control unit 192 stops the heat exchanger 500 by controlling the heat load side three-way valve 630 so that the flow rate of the cold water branched from the load side return path W 22 to the heat exchange path W 23 becomes zero.
  • step S 122 the driving control unit 192 waits for the lapse of the t 2 time (step S 122 ). After step S 122 , the process shifts to step S 131 .
  • the heat exchange path W 23 is provided in the load side return path W 22 , and the heat exchanger 500 exchanges heat between the heat exchange path W 23 and the cooling tower side outward path W 11 .
  • the heat load side three-way valve 630 is able to adjust the flow rate of the heat exchange path W 23 .
  • the heat exchanger 500 exchanges heat between the heat exchange path W 23 and the cooling tower side outward path W 11 , the temperature change due to the heat exchange does not occur after the cooling water passes through the cooling tower 410 .
  • the cooling tower bypass path W 13 is able to connect the cooling tower side outward path W 11 and the cooling tower side return path W 12 with each other, and the cooling tower side three-way valve 430 is able to adjust the flow rate of the cooling tower bypass path W 13 .
  • the heat exchanger 500 is disposed on a side of the turbo freezer 300 (an upstream side of a path of the cooling water) with respect to the cooling tower bypass path W 13 in the cooling tower side outward path W 11 .
  • the cooling water flows through the cooling tower side three-way valve 430 after the heat exchange in the heat exchanger 500 .
  • the temperature of the cooling water passing through the cooling tower side three-way valve 430 does not change through the heat exchanger 500 before reaching the condenser 340 .
  • the control unit 190 calculates the bypass amount of the cooling water on the basis of the temperature of the cooling water in the cooling tower side three-way valve 430 , it is not necessary to consider the temperature change of the cooling water due to the heat exchanger 500 . At this point, it is possible to avoid an increase of a load for which the control unit 190 calculates the bypass amount of the cooling water.
  • cooling water exchanges heat with the cold water in the heat exchanger 500 and is cooled, it is possible to effectively use the cold water.
  • the load determination unit 191 determines whether or not the load of the cold water supply to the heat load 610 is less than the load lower limit value. In a case in which the load determination unit 191 determines that the load of the cold water supply to the heat load 610 is less than the load lower limit value, the driving control unit 192 controls the heat load side three-way valve 630 to cause the heat exchanger 500 to perform the heat exchange.
  • the heat load side three-way valve 630 for adjusting the flow rate to the heat exchanger 500 is provided in the load side return path W 22 in the constitution example of FIG. 2 , the valve for adjusting the flow rate to the heat exchanger 500 may be provided on a side of the cooling tower side outward path W 11 . This point will be described with reference to FIG. 5 .
  • FIG. 5 is a schematic constitution diagram showing another example of the device constitution of the freezer plant main body 200 .
  • the freezer plant main body 200 includes a heat exchange three-way valve 240 , the turbo freezer 300 , the cooling tower 410 , the cooling water pump 420 , the cooling tower side three-way valve 430 , the heat exchanger 500 , the cold water pump 620 , the outward path side temperature sensor 711 , a return path side temperature sensor 712 , and the flow rate sensor 721 .
  • the turbo freezer 300 includes the evaporator 310 , the evaporator pump 320 , the turbo compressor 330 , the condenser 340 , the refrigerant pump 350 , and the expansion valve 360 .
  • freezer plant main body 200 is connected to the heat load 610 .
  • the heat exchanger 500 is provided in the cooling tower side outward path W 11 in the example of FIG. 2
  • the heat exchanger 500 is provided in the load side return path W 22 in the example of FIG. 5 .
  • the heat load side three-way valve 630 is provided in the load side return path W 22 , and the heat load side three-way valve 630 and the heat exchanger 500 are connected with each other by the heat exchange path W 23 .
  • the heat exchange three-way valve 240 is provided in the cooling tower side outward path W 11 , and the heat exchange three-way valve 240 and the heat exchanger 500 are connected with each other by a heat exchange path W 14 .
  • the other points are the same as in the case of FIG. 2 .
  • the heat exchange three-way valve 240 corresponds to an example of the heat exchange three-way valve, and adjusts the amount of the cooling water branched from the cooling tower side outward path W 11 to the heat exchange path W 14 .
  • the heat exchange three-way valve 240 is provided an upstream side of the cooling tower side three-way valve 430 in the cooling tower side outward path W 11 .
  • the upstream side of the cooling tower side three-way valve 430 in the cooling tower side outward path W 11 is a side closer to the turbo freezer 300 than the cooling tower side three-way valve 430 as viewed from the turbo freezer 300 .
  • the heat exchange path W 14 is provided in the cooling tower side outward path W 11 , and the heat exchanger 500 exchanges heat between the heat exchange path W 23 and the load side return path W 22 .
  • the heat exchange three-way valve 240 is able to adjust the flow rate of the heat exchange path W 14 .
  • the heat exchanger 500 exchanges heat between the heat exchange path W 14 and the load side return path W 22 , and the heat exchange path W 14 is provided in the cooling tower side outward path W 11 . Therefore, the temperature change of the cooling water due to the heat exchange does not occur after passing through the cooling tower 410 . In this point, in the heat source system 1 , it is possible to relatively simply perform the temperature control of the cooling water. Therefore, in the heat source system 1 , it is possible to continue the driving of the turbo freezer 300 even in a case in which the cold heat amount required by the heat load 610 is small, and it is possible to relatively simply perform the temperature control of the cooling water.
  • the heat exchange path W 14 is provided on a side of the turbo freezer 300 (the upstream side of the path of the cooling water) with respect to the cooling tower bypass path W 13 in the cooling tower side outward path W 11 .
  • the cooling water branched to the heat exchange path W 14 flows through the cooling tower side three-way valve 430 after the heat exchange in the heat exchanger 500 .
  • the temperature of the cooling water passing through the cooling tower side three-way valve 430 does not change through the heat exchanger 500 before reaching the condenser 340 .
  • the control unit 190 calculates the bypass amount of the cooling water on the basis of the temperature of the cooling water in the cooling tower side three-way valve 430 , it is not necessary to consider the temperature change of the cooling water due to the heat exchanger 500 . At this point, it is possible to avoid an increase of a load for which the control unit 190 calculates the bypass amount of the cooling water.
  • cooling water exchanges heat with the cold water in the heat exchanger 500 and is cooled, it is possible to effectively use the cold water.
  • each unit may be performed by recording a program for realizing all or a part of the functions of the control unit 190 in a computer-readable recording medium, and causing a computer system to read and execute the program recorded in the recording medium.
  • the “computer system” referred to here is presumed to include an OS or hardware such as a peripheral device.
  • the “computer-readable recording medium” refers to a storage device such as a portable medium such as a flexible disk, a magneto-optical disc, a ROM, and a CD-ROM, or a hard disc that is installed inside the computer system.
  • the program may be for realizing a part of the functions described above, or may be realized in combination with the program in which the functions described above is already recorded in the computer system.
  • An embodiment of the present invention relates to a heat source system including a heat source machine, a cooling tower side outward path and a cooling tower side return path that are connected to the heat source machine, a load side outward path and a load side return path that are connected to the heat source machine, a heat exchange path provided in one of the load side return path and the cooling tower side outward path, a heat exchanger that performs heat exchange between the heat exchange path and the other one of the load side return path and the cooling tower side outward path, and a heat exchange adjustment valve capable of adjusting a flow rate of the heat exchange path.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
US16/467,011 2016-12-07 2017-12-07 Heat source system, control device, control method, and program Abandoned US20190301777A1 (en)

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JP2016-237379 2016-12-07
PCT/JP2017/044061 WO2018105702A1 (ja) 2016-12-07 2017-12-07 熱源システム、制御装置、制御方法及びプログラム

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Publication number Priority date Publication date Assignee Title
DE102020110357A1 (de) 2020-04-16 2021-10-21 Wolfram Ungermann Systemkälte GmbH & Co. KG Verfahren zur Regelung eines hybriden Kühlsystems sowie hybrides Kühlsystem
DE102020110357B4 (de) 2020-04-16 2024-06-20 Wolfram Ungermann Systemkälte GmbH & Co. KG Verfahren zur Regelung eines hybriden Kühlsystems

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